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WO1996007058A1 - Capteur de temperature d'air moyenne - Google Patents

Capteur de temperature d'air moyenne Download PDF

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Publication number
WO1996007058A1
WO1996007058A1 PCT/US1995/010067 US9510067W WO9607058A1 WO 1996007058 A1 WO1996007058 A1 WO 1996007058A1 US 9510067 W US9510067 W US 9510067W WO 9607058 A1 WO9607058 A1 WO 9607058A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
pressure region
high pressure
temperature sensor
average temperature
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US1995/010067
Other languages
English (en)
Inventor
Joe M. Baldwin
Dale C. Cotton
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Trane US Inc
Original Assignee
American Standard Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by American Standard Inc filed Critical American Standard Inc
Priority to AU34903/95A priority Critical patent/AU3490395A/en
Priority to CA002198083A priority patent/CA2198083C/fr
Priority to GB9702146A priority patent/GB2305501B/en
Publication of WO1996007058A1 publication Critical patent/WO1996007058A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01K—MEASURING TEMPERATURE; MEASURING QUANTITY OF HEAT; THERMALLY-SENSITIVE ELEMENTS NOT OTHERWISE PROVIDED FOR
    • G01K3/00—Thermometers giving results other than momentary value of temperature
    • G01K3/02—Thermometers giving results other than momentary value of temperature giving means values; giving integrated values
    • G01K3/06—Thermometers giving results other than momentary value of temperature giving means values; giving integrated values in respect of space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/0001—Control or safety arrangements for ventilation
    • F24F2011/0002—Control or safety arrangements for ventilation for admittance of outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S236/00—Automatic temperature and humidity regulation
    • Y10S236/19—Ventilated thermostat

Definitions

  • the present invention relates generally to air conditioning systems for buildings. More particularly it pertains to a supply air temperature sensor capable of sensing the average temperature of the supply air being supplied to a heating or cooling zone. In alternate embodiments, the location of the sensor can be shifted to measure outside air temperature. In further alternative embodiments, humidity, carbon dioxide or indoor air quality sensors may be substituted for or combined with the air temperature sensor.
  • roof top units are characterized as forced air units that distribute the conditioned air (either heated or cooled) by means of fans, through supply ducts, to each of the ventilated zones of a building.
  • the systems are semi-closed loop systems in the sense that conditioned air is circulated to the zones of a building to cool or heat the zones, and then is returned by return ducts to the heating or refrigeration system to be heated or cooled and recirculated to the zones .
  • Outdoor ambient air may be admitted for cooling purposes or to maintain an adequate indoor air quality, as will be further explained.
  • the most recent roof top designs are variable air volume (VAV) systems.
  • VAV variable air volume
  • VAV systems are designed to operate at a constant supply air temperature, for example, 55°F.
  • the volume of the supply air provided to the ventilated zones of the building is varied in order to satisfy particular cooling or heating requirements, but the temperature of the air is maintained constant.
  • a high volume of cooled air at 55°F would be needed to satisfy the cooling requirements.
  • a substantially reduced volume of cooled air at 55° would be required to meet design cooling requirements.
  • the operating speeds of fans in a VAV system are varied to vary the volume of conditioned air that is being supplied to the various zones at any given time, thereby keeping the temperature of the zones at a desired setpoint temperature of, for example, 72°F as sensed by the thermostat in the zone.
  • the 55° supply air temperature and the sensed temperature in the zone become controlling factors for the VAV system.
  • the first VAV air conditioning systems provided all cooling by mechanical means. Thus, the compressor and the heat exchange coil were required to be operated frequently in order to cool the air distributed throughout a building. This was true even when the outside ambient air was relatively cool. The compressors require relatively large amounts of energy for operation. As ways were sought to improve the efficiency and reduce the cost of cooling air, economizers were designed and installed on air conditioning systems.
  • An economizer is a device that introduces outside air into the system to provide cooling when the ambient air has an energy level that makes this possible. Since VAV systems always supply air at a constant temperature of nominally 55°F, outside air is generally effective to assist in cooling at all times that the outside air temperature is less than 55°F. Outside air is mixed by an economizer in a VAV
  • the outside air is provided by the fans as cooled supply air to the ventilated zones. It will be appreciated that, as the temperature of the outside air is reduced, a much reduced volume of outside air is needed to cool the zones to a desired temperature. When the outside air is, for example, 10°F, very little outside air needs to be added to the return air to reduce the return air to 55°F and to keep the zones at 72°F. In such conditions, the total air flow through the air conditioning system can typically be less than one third of the air conditioning system's full capacity, which occurs during 100- mechanical cooling.
  • VAV systems that are of a side-by-side ' design.
  • Side-by-side VAV systems are designed to have return air enter the rooftop unit on one side of the unit and tne outside air enter on the other side, as opposed to the "over and under" orientation of previous designs.
  • the return air and the outside air each pass through a damper assembly and enter a common plenum, where mixing should occur.
  • Side-by-side designs are preferable in that the air that is directed onto the coils of the evaporator is more uniform m temperature from the top to the bottom of the unit.
  • the side-by-side design corrects some freezing problems experienced in the heat exchange coil with over-and-under designs.
  • the side-by-side design results in the fans drawing the return air and the outside air through the plenum of the rooftop unit in unmixed parallel, side-by-side flows.
  • the air then enters the descending supply ducts in a stratified, unmixed manner.
  • stratification is even further exacerbated as rooftop designs are made ever wider in order to add additional cooling capacity.
  • Current VAV systems may be between four and ten feet wide. The plenum necessarily becomes wider, making it more difficult to effect adequate mixing under low flow conditions.
  • the temperature of the supply air as the supply air enters the main supply duct is an important controlling parameter for the VAV system. Measurement of the temperature is typically accomplished by means of a thermistor.
  • the output of a thermistor is a resistance that varies with temperature.
  • a grid including a plurality of thermistors has been constructed utilizing pairs of series ana parallel connected thermistors.
  • an equal number of series pairs of thermistors and parallel pairs of thermistors must be coupled together to obtain the desired averaging. Accordingly, the system may employ a single thermistor, or grids of four, eight, sixteen, etc. thermistors as desired to obtain the average temperature.
  • the present invention meets the foregoing objectives by providing a flow tube in which a flow of average temperature air is induced by being disposed in a high pressure region and having air inlets therein and an air outlet in a low pressure region.
  • the air inlets are so disposed to intercept a representative sample of the air in the high pressure region.
  • This air is mixed in the flow tube to provide an average temperature thereof.
  • a single temperature sensor is disposed relative to the flow tube to sense the temperature of the mixed air flowing therein. The use of a single temperature sensor greatly simplifies fault detection and correction.
  • the flow tube utilized may be a readily available, commercial grade copper tube. Installation of the flow tube m the air conditioning is very simply accomplished, avoiding the need for the construction and installation of a sensor grid and supporting lattice work.
  • the air inlets are all of the same diameter, making their formation relatively simple. The end result is a simple, reliable, inexpensive sensor system that adequately senses the average temperature of the supply air, which is a critical control variable for the air conditioning unit.
  • the average temperature sensor is designed for use in an air conditioning unit, wherein the air conditioning unit has a high pressure region and a low pressure region.
  • the average temperature sensor senses the average temperature of air flowing in the high pressure region and comprises a device for conveying a flow of air that is in fluid communication with the high pressure region and the low pressure region and a temperature sensor that is disposed in a temperature sensing relationship to the device for conveying a flow of air in order to sense the temperature of the flow of air therein.
  • the high pressure in the high pressure region induces a flow of air in the device for conveying a flow of air, which flow of air flows from the high pressure region to the low pressure region and is at the average temperature of the air m the high pressure region.
  • the device for conveying a flow of air includes a plurality of air inlets selectively disposed within the high pressure region to receive a sample flow of air that has a temperature that is representative of the average temperature of the air flowing in the high pressure region. Both the arrangement of the inlet and the location of the device can be varied.
  • Figure 1 is a top perspective view of a rooftop air conditioning system having an average temperature sensor assembly n accordance with the present invention installed therein, and with a portion of the exterior housing enclosure broken away to reveal the inner mechanisms of the system;
  • Figure 2 is a top perspective view of the supply air portion of a rooftop air conditioning system having an average temperature sensor assembly in accordance with the present invention installed therein;
  • Figure 3 is a sectional view of an average temperature sensor assembly taken along line 3-3 of Figure 2;
  • Figure 4 is a sectional view of an average temperature sensor assembly taken along line 4-4 of Figure 3.
  • Figure 5 is an alternative embodiment of the present invention and is used to measure outside air temperature.
  • air conditioning unit 10 includes a sheet metal housing 12 of generally rectangular configuration adapted for mounting on the roof of a building and enclosing the various mechanical and electrical components of unit 10.
  • Housing 12 generally provides for a weather-tight enclosure that shelters the various mechanical components of the unit 10 from the elements. Housing 12 is designed to be installed on a rooftop and then left in the elements for many years of operation. A number of access panels (not shown) are included in housing 12 to provide maintenance access to the mechanical and electrical components housed therein.
  • Representative air conditioning units 10 are shown in applicant's U.S. Patents 5,324,229 to Weisbecker; 4,679,411 to Pearse, Jr.; 4,501,125 to Han; and 4,353,409 to Saunders et al., all of which are incorporated herein by reference.
  • Air conditioning unit 10 is an air recirculating type of device. Accordingly, air flows generally from a first end (at the left of the depiction of Figure 1) of air conditioning unit 10 to second end thereof (at tne right of the depiction of Figure 1), where the conditione ⁇ supply a r is circulated to the various heating and cooling zones of the building. Return air from the zones of the building enters the unit 10 at the first end thereof for recooling or reheating, as desired, and recirculation to the zones.
  • Air conditioning unit 10 includes an outside air inlet opening 14. Outside air inlet opening 14 is fluidly coupled to an outside air chamber 16 defined within unit 10.
  • the outside air inlet opening 14 typically includes a grillwork that extends across opening 14 to minimize the intrusion of debris therein.
  • Outside air chamber 16 is preferably a relatively large plenum that acts to straighten the flow of outside air into the remaining portions of unit 10. The flow of outside air is indicated in Figure 1 by arrow OA.
  • Return air chamber 20 is disposed alongside outside air chamber 16.
  • a return air duct opening 18 is located in the bottom wall of housing 12. The return air duct opening 18 is upwardly directed to facilitate the flow of return air into return air chamber 20.
  • the return air duct opening 18 is in flow communication with the return air duct work (not shown) of the building that is being cooled or heated. Return air flows upward from the zones of the building into return air chamber 20 as indicated by arrow RA. Return air chamber 20 and outside air chamber 16 are separated by a fluid tight partition 22, such that there is no mixing of outside air and return air at this stage of unit 10.
  • the return air chamber 20 may include a return air exhaust ports 24. Under certain circumstances, it is desirable to exhaust a portion of the return air to the atmosphere rather than recooling such air and recirculating it to the building zones. Exhausting of the return air may be facilitated by centrifugal fans 26, 28. Fans 26, 28 are powered on a common drive shaft 30 by motor 32, acting through belt and pulley system 34.
  • Figure 1 illustrates the side by side arrangement of the outside air and return air pathways that is favored in the design of the VAV type air conditioning units 10. Such units 10 are designed to have a relatively reduced height dimension of three to four feet as compares to the width dimension, which may be ten feet or more in order to accommodate greater volumes of air and increased heating and cooling capacity.
  • a common filter plenum 36 is fluidly coupled to both the outside air chamber 16 and the return air chamber 20.
  • the flow of outside air and return air into common filter plenum 36 is controlled by damper assemblies 38, 40.
  • Damper assemblies 38, 40 are preferably moveable to independently control the flow of outside air and return air into common filter plenum 36 as desired. For example, during periods of operation in which all the return air is being exhausted by fans 26, 28, the damper assembly 40 will be in the closed position.
  • the mixing ratio of return air and outside air is typically a function of the enthalpy of the outside air as compared to the enthalpy of the return air and the need to intake fresh outside air m order to maintain the indoor air quality at a desired level.
  • the common filter plenum 36 contains filters 42.
  • the filters 42 are of the flow through type, such that the outside air and return air flow from the left to the right as depicted in Figure 1 during the filtration process. Filters 42 may be readily replaced as needed.
  • Heat exchange coil 44 provides for conditioning of the air flowing therethrough by connection to a source of steam or heated or chilled water, to the evaporator of a direct expansion refrigeration system, to the indoor coil of a vapor-compression type heat pump system or to any other known heating or cooling device or medium.
  • the air flowing through the heat exchange coil 44 is conditioned (heated or cooled) as desired and is thereafter known as the supply air.
  • the supply air is captured by fans 46, 48.
  • the fans 46, 48 are powered by a common shaft 50 that is in turn driven through the belt and pulley system 52 by motor 5 .
  • Other motor, driving and shaft arrangements are also contemplated.
  • the fans 46, 48 each have inlets (not shown) that are located in the side portions thereof to facilitate the entry of the supply air as indicated by the arrows SA1.
  • the fans 46, 48 each have exhausts 56 that discharge the accelerated supply air as indicated m Figure 1 by the arrows SA2.
  • the inlets of the fans 46, 48 are fluidly separated from the exhausts 56 thereof by plenum wall 58.
  • Plenum wall 58 fluidly separates the common filter plenum 36 from the supply air plenum 60.
  • Supply air plenum 60 is fluidly coupled to the supply duct work that supplies conditioned air to the building zones by supply air duct mouth 62 formed in the portion of the bottom side of housing 12 that forms the bottom of supply air plenum 60.
  • the supply air duct mouth 62 has a width that is somewhat less than the width of the supply air plenum 60 as measured from the interior sidewalls 64, but that spans a substantial portion of the distance between the interior sidewalls 64.
  • the supply air is made up of return air and outside air. Without adequate mixing of the return air and the outside air, the supply air becomes stratified, with the outside air entering the upper portion of the supply air duct mouth 62 and the return air entering the lower portion of the supply air duct mouth 62, as depicted in Figure 1. The aforementioned stratif cation of the supply air is evidenced as a varying temperature across the width of the supply air duct mouth 62.
  • the present invention utilizes a flow tube 66 to make the average supply air temperature measurement.
  • the flow tube 66 is preferably an L shaped tube having a first leg 68 that is disposed to span substantially the full width of the supply air duct mouth 62 and a second leg 70 that fluidly couples the first leg 68 to the common filter plenum 36.
  • the flow tube 66 preferably has a circular cross section and is made of a relatively tmn walled metallic material, such as copper.
  • the inside diameter of the flow tube 66 is preferably approximately 1 inch (2.54 cm) in diameter, but the flow tube may have an inside diameter of between 1/4 inch to 2 inches (.635 cm to 5.08 cm) .
  • the inside diameter is preferably constant throughout the full span of flow tube 66 although graduated tubing or the like may be used if desired. This permits the use of readily available copper tubing having such constant inside diameter in the construction of flow tube 66.
  • the first leg 68 of the flow tube 66 is fluidly sealed at the end 72.
  • a series of air inlets 74 are formed in the wall of flow tube 66.
  • the air inlets 74 extend from the exterior of flow tube 66 through the wall thereof to the interior air passageway that is formed by flow tube 66. In a preferred embodiment, the total area of all the air inlets 74 is less than the cross sectional area formed by the inside diameter of flow tube 66. This aids in generating an efficient air flow in flow tube 66.
  • the spacing of the air inlets 74 along the flow tube 66 is dependent on the distance of a given air inlet 74 from the open end 76 of the second leg 70 of flow tube 66.
  • the spacing between adjacent air inlets 74 is less the further the specific air inlet 74 is from the open end 76.
  • This reduced spacing accounts for the reduced pressure differential that exists at the air inlets 74 that are more distant from open end 76 and ensures approximately equal air flow from all portions of first leg 68 of flow tube 66.
  • the air inlets 74 can be regularly spaced along the flow tube 66 and the area of the air inlets 74 can be increased with the proximity of the respective air inlet 74 to the end 72.
  • the arrangement of the air inlets 74 is preferably linear and facing into the airflow, although non-linear arrangements spiralmg around or spaced irregularly around the flow tube 66 are also contemplated.
  • the air inlets 74 are preferably directed to open into the flow of supply air in order to facilitate the flow of supply air therethrough.
  • the air inlets 74 are upwardly directed, since the flow of supply air is downward into supply air duct mouth 62.
  • the length of the first leg 68 of the flow tube 66 is readily a ⁇ apted to the various widths of the supply duct mouth 62 found in air conditioning units 10 of varying width.
  • end 76 of second leg 70 is open. Additionally, end 76 is open into common filter plenum 36.
  • Flow tube 66 projects through an opening (not shown) m plenum wall 58. The outside surface of flow tube 66 is in sealing engagement with the plenum wall 58 that fluidly separates the common filter plenum 36 from the supply air plenum 60 in order to maintain a fluid tight seal therebetween. The described seal is maintained at the point of intersection, indicated at 78.
  • a single temperature sensor 80 is installed within the second leg 70 of flow tube 66.
  • the temperature sensor 80 is preferably disposed proximate the end 76 of the second leg 70 and positioned to be affected by the flow of air in flow tube 66.
  • the temperature sensor 80 is preferably of the thermistor, bulb type, in which the temperature is represented by the varying resistance of the sensor 80. Such resistance changes as a function of the sensed temperature of the air flowing past sensor 80.
  • a lead 82 passes tnrough the wall of flow tube 66 and is connected to the control system (not shown) of the air conditioning unit 10. It is understood that other types of temperature sensors may be satisfactorily utilized. Such temperature sensors may disposed either vasively or noninvasively with respect to flow tube 66.
  • FIG. 2 depicts an alternative configuration of supply air plenum 60 of air conditioning unit 10 with a flow tube 66 of the present invention installed therein.
  • Supply air plenum 60 has a supply air duct mouth 62 formed in the bottom wall thereof.
  • Supply air duct mouth 62 is rectangular in shape and bounded by first opposed sides 84, 86 and second opposed sides 88, 90.
  • the supply air plenum 60 as depicted in Figure 2 is designed for use with an air conditioning unit 10 that provides between 20 and 50 tons of cooling capacity. Such capacity requires a generous opening at supply air duct mouth 62.
  • first opposed sides 84, 86 are approximately five feet m length and second opposed sides 88, 90 are approximately three feet in length.
  • Flow tube 66 preferably has an outside diameter of .875 inches and an inside diameter of .785 inches.
  • Flow tube 66 is suspended on brackets 92, 94 such that the first leg 68 of flow tube 66 spans substantially the full, long dimension of supply air duct mouth 62 as defined by first opposed sides 84, 86.
  • First leg 68 of flow tube 66 is substantially parallel with the first opposed sides 84, 86 of supply air duct mouth 62.
  • Flow tube 66 has a right angle bend 96 that is located proximate second opposed side 88.
  • Right angle bend 96 defines the juncture of first leg 68 and second leg 70 of flow tube 66.
  • first leg 68 of flow tube 66 is approximately five feet in length.
  • First leg 68 includes a plurality of upwardly directed air inlets 74.
  • Group 100 is located closest to the reduced pressure that is in filter plenum 36.
  • Group 100 consists of a single air inlet 74 and experiences the greatest pressure differential of all the air lets 74 disposed along first leg 68.
  • Group 102 consists of two air inlets 74.
  • the air inlets 74 of group 102 are disposed approximately three inches from each other and are preferably one foot upstream (toward sealed end 72) from the air inlet 74 of group 100.
  • Group 104 is comprised of three air inlets 74. They are located approximately three inches apart. Group 104 is located approximately one foot upstream from group 102.
  • the final group of air mlets 74 is group 106.
  • Group 106 is comprised of three air inlets 74 that are located approximately three inches apart. Group 106 is located approximately one foot upstream from group 104.
  • the rightmost air inlet 74 of group 106 is the furthest air inlet 74 from the reduced air pressure that exists filter plenum 36.
  • each of the air mlets will experience the least differential pressure and the least air flow therethrough as compared to the other air lets 74.
  • the spacing of the groups 100, 102, 104, and 106 along the span of first leg 68 in conjunction with the generally increasing number of air inlets 74 in each such group compensates for the decreased pressure differential and the air flow that exists in the upstream direction in flow tube 66.
  • each of the air mlets each of the air mlets
  • the second leg 70 of flow tube 66 is relatively short in length as compared to first leg 68. Second leg 70 in the embodiment depicted is approximately one foot in length. Second leg 70 includes mounting bore 108 for the mounting of temperature sensor 80 therein.
  • a plastic tube 110 is utilized to fluidly connect flow tube 66 to filter plenum 66.
  • Plastic tube 110 is slipped over the end of second leg 70 and affixed thereto by a wire tie or a hose type clamp.
  • Plastic tube 110 is sealably coupled to plenum wall 58 at 78 by a bushing 112 disposed in plenum wall 58.
  • the open end 76 of plastic tube 110 opens into filter plenum 36.
  • Figure 3 is a depiction of second end 70 of flow tube 66 coupled to plastic tube 110.
  • Flow tube 66 is supported approximately three inches above second opposed side 88 of supply air duct mouth 62 by bracket 92.
  • Flow tube 66 is retained atop bracket 92 by clamps 113.
  • Clamps 113 are metallic and have an inner rubber grommet that absorbs vibration generated by the operation of air conditioning unit 10. Temperature sensor 80 is depicted disposed within mounting bore 108 such that the portion of temperature sensor 108 depicted in phantom protrudes into the interior air passageway of flow tube 66. Lead 82 is shown held in place on flow tube
  • Plastic tube 110 is shown slipped over the end of second leg 70 of flow tube 66.
  • Plastic tube 110 has an inside diameter that is very slightly greater tnan the outside diameter of flow tube 66, in order to facilitate the rea ⁇ y emplacement of plastic tube 110 on flow tube 66.
  • Plastic tube 110 is relatively resilient and is bendable through shallow angles. Such shallow angle bends do not materially alter the inside diameter of plastic tube 110. Thus, plastic tube 110 can be routed around any intervening machinery and yet not affect the flow of supply air therein.
  • Figure 4 depicts flow tube 66 mounted to bracket 92.
  • Clamp 113 is shown surrounding the exterior diameter of flow tube 66 with a tail that is secured to bracket 92 by sheet metal screw 116.
  • Temperature sensor 80 is shown disposed partially within the interior area of flow tube 66.
  • An expandable, rubberized retaining wrap 118 is positioned around temperature sensor 80 and the underside of flow tube 66 to retain temperature sensor 80 therein.
  • Bracket 92 is depicted affixed to the edge of second opposed side 88 of supply air duct mouth 62 in a conventional manner by sheet metal screw 116.
  • supply air is taken into fans 46, 48 through air inlets and accelerated thereby.
  • return air and outside air are thoroughly mixed in common filter plenum 36. This is rarely the case m practice, however. In practice, the supply air may be stratified and exhibit a non uniform temperature throughout, as previously described.
  • the accelerated supply air, SA2 is discharged from the fans 46, 48 into supply plenum 60.
  • the operation of the fans 46, 48 m drawing supply air from the common filter plenum 36 and ejecting the supply air into the supply plenum 66 at relatively high velocity creates a condition of higher air pressure in the supply plenum 60 than exists n the common filter plenum 36.
  • the higher pressure in the supply plenum 60 induces the flow of supply air in the flow tube 66.
  • the fans 46, 48 act as pumps to pump a flow of supply air into air mlets 74 and through the flow tube 66, past temperature sensor 80 to exhaust into common filter plenum 36.
  • the flow of supply air is drawn from the air mlets 74, displaced across the full span of first leg 68.
  • the aforementioned spacing of the air lets 74 ensures that the amount of air drawn from the furthest portion thereof, proximate air inlet 74b, as depicted in Figure 1, is approximately the same as that which is drawn from the portion nearest outlet 76, proximate first air inlet 74a.
  • Such spacing accounts for the lesser pressure differential that results proximate the air inlet 74b as compared to the air inlet 74a and ensures that the air flow m flow tube 66 is representative of the average supply air that is entering the air supply duct mouth 62.
  • the air flow m flow tube 66 is representative of the average supply air that is entering the air supply duct mouth 62.
  • Such thorough mixing results in the temperature of the air flow as sensed by sensor 80 being the average temperature of the supply air.
  • the diameter of the flow tube 66 is selected based on tests with a given air conditioning unit 10 under all operating conditions. The diameter is adequate to ensure adequate flow over the sensor 80 to sense the average temperature of the supply air, even when the fans 46, 48 are operating at less than the designed minimum operating conditions. Such conditions result in the least pressure differential between the supply plenum 60 and the common filter plenum 36. It is under such conditions that the least air flow is induced in the flow tube 66.
  • Figure 5 is an alternative embodiment of the present invention where the location of the flow tube 200 is moved to measure outside air. This is accomplished by positioning the flow tube 200 through an aperture 202 in the housing 12 and locating the flow tube 200 in the return air chamber 20. An outside end 204 of the flow tube 200 projects through the housing 12 and is open to outside air. A screen 206 prevents objects from entering the flow tube 200 through the open outside end 204.
  • the flow tube 200 is formed with a P-trap 208 to prevent condensate from entering the air conditioning unit 10. Since air is being exhausted from the return air chamber 20 through the exhaust ports 24, the pressure m the return air chamber 20 is low relative to the pressure of the outside air.
  • an interior end 210 of the flow tube 200 is located adjacent the return air stream so that the return air stream pulls air from the flow tube 200 by induction. This causes a flow of outside air through the open outside air end 204 across the temperature sensor 80 and through the end 210 into the return air stream.
  • the temperature sensor 80 can be positioned anywhere in the flow tube 200 and the outside air temperature need not be averaged since it is presumed to be thoroughly mixed.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Air Conditioning Control Device (AREA)
  • Measuring Temperature Or Quantity Of Heat (AREA)

Abstract

Capteur de température moyenne pour unité de conditionnement d'air présentant une zone haute pression et une zone basse pression, et procédé pour effectuer des mesures de température moyenne. Ledit capteur détectant la température moyenne de l'air s'écoulant dans la zone haute pression comporte un dispositif de transport d'un écoulement d'air en communication fluidique avec ladite zone. Le capteur est disposé dans ledit dispositif de manière à pouvoir y mesurer la température de l'écoulement d'air. La pression élevée de la zone haute pression engendre un écoulement d'air dans le dispositif de transport d'écoulement d'air, ce dernier se dirigeant de la zone haute pression vers la zone basse pression, et présentant une température moyenne qui est la température ambiante de la zone haute pression. Ledit dispositif comporte une série d'entrées d'air disposées sélectivement dans la zone haute pression pour recevoir un écoulement d'air échantillon dont la température est représentative de la température moyenne de l'air circulant dans la zone haute pression.
PCT/US1995/010067 1994-08-26 1995-08-08 Capteur de temperature d'air moyenne Ceased WO1996007058A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU34903/95A AU3490395A (en) 1994-08-26 1995-08-08 Average air temperature sensor
CA002198083A CA2198083C (fr) 1994-08-26 1995-08-08 Detecteur de temperature moyenne de l'air
GB9702146A GB2305501B (en) 1994-08-26 1995-08-08 Air conditioning units

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US08/296,850 US5533348A (en) 1994-08-26 1994-08-26 Average air temperature sensor
US08/296,850 1994-08-26

Publications (1)

Publication Number Publication Date
WO1996007058A1 true WO1996007058A1 (fr) 1996-03-07

Family

ID=23143839

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1995/010067 Ceased WO1996007058A1 (fr) 1994-08-26 1995-08-08 Capteur de temperature d'air moyenne

Country Status (5)

Country Link
US (1) US5533348A (fr)
AU (1) AU3490395A (fr)
CA (1) CA2198083C (fr)
GB (1) GB2305501B (fr)
WO (1) WO1996007058A1 (fr)

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ES2340654A1 (es) * 2008-12-05 2010-06-07 Rafael POLANCO MUÑOZ Instalacion para la unificacion de la temperatura en un recinto.
US10330328B2 (en) 2013-07-22 2019-06-25 Trane International Inc. Temperature control system

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US7493193B2 (en) * 2005-08-04 2009-02-17 International Business Machines Corporation Monitoring and real-time heat load control based upon server and environmental parameters
JP6100523B2 (ja) * 2012-12-28 2017-03-22 株式会社Ｎｔｔファシリティーズ 冷水循環システム
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US10154614B1 (en) * 2014-06-04 2018-12-11 Amazon Technologies, Inc. Air handling unit intake air preheat system and method
US9835347B2 (en) 2014-12-08 2017-12-05 Johnson Controls Technology Company State-based control in an air handling unit
US10921017B2 (en) * 2015-07-09 2021-02-16 Trane International Inc. Systems, aparatuses, and methods of air circulations using compact economizers
CN108289220B (zh) * 2018-01-15 2020-11-27 深圳市奥拓电子股份有限公司 虚拟图像处理方法、图像处理系统及存储介质
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Publication number Priority date Publication date Assignee Title
ES2340654A1 (es) * 2008-12-05 2010-06-07 Rafael POLANCO MUÑOZ Instalacion para la unificacion de la temperatura en un recinto.
WO2010063864A1 (fr) * 2008-12-05 2010-06-10 Polanco Munoz Rafael Installation permettant d'uniformiser la température dans une enceinte
ES2340654B1 (es) * 2008-12-05 2011-06-15 Rafael POLANCO MUÑOZ Instalacion para la unificacion de la temperatura en un recinto.
US10330328B2 (en) 2013-07-22 2019-06-25 Trane International Inc. Temperature control system

Also Published As

Publication number Publication date
GB2305501A (en) 1997-04-09
GB2305501B (en) 1998-10-21
GB9702146D0 (en) 1997-03-26
AU3490395A (en) 1996-03-22
CA2198083C (fr) 2000-01-18
CA2198083A1 (fr) 1996-03-07
US5533348A (en) 1996-07-09

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